US1540124A - Variable-speed transmission mechanism - Google Patents

Description

F. A. HAYES VARIABLE SPEED TRANSMISSIQN MECHANISM June 2,

Filed March 14, 1921 wueutoz June 2,. I

: F. A. HAYES VARIABLE SPEED TRANSMISSION MECHANISM I 10 Sheets-Sheet 2 Filed March 14, 1921 WWW (inventor,

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F. A. HAYES VARIABLE SPEED TRANSMISSION MEGQANISM Filed March 14, 1921 10 Sheets-Sheet 1 @f t; e l-07 h Q6 June 2, 1925..

F. A. HAYES VARIABLE SPEED TRANSMISSION MECHANISM Filed March 14, 1921 10 Sheets-Sheet a June 2, 1,540,124

F. A. HAYES- VARIABLE SPEED TRANSMISSION MECHANISM Filed March 14, 1921 10 Sheets-Sheet 9 mum Tn iii' J um v F. A. HAYES VARIABLE SPEED TRANSMISSION MECHANISM Filed March 14, 1921 10 Sheets-Sheet 10 Patented 1...... 2, 1925.

UNITED STATES PATENT OFFICE. 1

FRANK A. HAYES, OF NEW YORK, N. Y.

VARIABLE-SPEED TRANSMISSION MECHANISM.

'Application filed March 14, 1921. Serial No. 452,305.

To all whom it may concern:

Be it known that I, FRANK A. HAYES, a citizen of the United States of America, residing at New York, in thecounty and State of New York, have invented certain new and useful Improvements in Variable-Speed Transmission- Mechanism, of which ,the following is a full, clear, and exact description.

This invention relates to variable-speed power-transmission mechanismof the sliding gear type, and its chief object, briefly stated, is to provide apparatus in which the shifting of the gears into mesh can beefi'ected only when the pitch-line velocities of the gears have a predetermined ratio, preferablynear unity; Another object is to provide an apparatus in which the shifting of the gears at the predetermined velocity-ratio is effected automatically by the energy which is driving one or another of the gears. To these'and other ends theinvention consists in the novel features of construction and combinations of elements hereinafter described.

' It is believed that the invention will its chief utility, in the automotive field, and accordingly in the subjoined description it will be explained and discussed with referenceto that use, with the understanding, however, that it is not limited thereto.

In the conventional automobile transmission of the sliding gear type,'proper gearshifting involves no less than six operations: (1) close throttle, (2) release clutch, (3

speed,'(5) open throttle, (6) engage clutch. Even to the skilled driver this complex'series of operations, which must be performed in proper sequence and with considerable care, involves a distinct expenditure of nerve energy, even though he may be unconscious of the fact, and hence adds materially to the fatigue and danger of driving. To the novice the operations are difficult to master and greatly increase the dangers of learning to drive a car. Many persons who do not pos-' sess a natural mechanical aptitude never really master the art of changing speeds with the conventionaltransmission. Onthe other hand, in the present embodiment of my invention gear shifting while the car is in motion is e ected by actuation of the engine throttle, all other operations following automatically upon the movement of the IDylIIVQIItlOIL 1 Fig. 3 is an end elevatlonof themecha throttle and'the resulting change of enginespeed.

In its preferred form, herein described, my invention possesses a number of impor-. tant advantages, such as ease and simplicity of operation, with practically no skill required on the part ofthe driver; greater safety in driving, since both hands are left entirely free for steering during speed changes; damage to the mechanism isvirtually impossible in shifting; ability to shift at high car speeds; rapidity of shifting, thus greatly increasing car acceleration or getaway; quick and easy changing on hills, thereby increasing hill-climbing ability; not necessary to disengage clutch to permit free coasting, and any desired speed can be applied with ease after a coast; reduction of wear on clutch plates or lining because of less frequent release and engagement of clutch.

My invention in its preferred form utilizes two important features conjointly.

One causes the gears to mesh and unmesh themselves, This effect is. produced by the use of helical-tooth gears, or'by the use of helical splines on the sliding-gear shaft, so

that the sliding gear will be screwed, as it were, out of or into mesh according to which gear (the sliding gear or the axially stationary gear) is tending to drive the other.

rotating at the same pitch-line velocity or shift out of one speed, (4) shift into desired accompanying drawings,

in which the preferred embodiment is shown, 1

Fig. 1 isa plan View of an axially-stationary gear, and of a gear slidable axially on a helically splined shaft, illustrating the self-meshing and unmeshing feature of the invention; p i

Fig. 2 is a diagrammatic plan view of a conventional sliding-gear transmission, combined'with the above mentioned features of nism shown in Fig; 2, viewed from the lower end of the figure.

Fig. 3, is a diagrammatic end View illustrating the operation of the selector mechanism.

Fig. 4 is aside View, partly in section, of an automobile transmission combined with my invention.

Fig. 5 is a cross section about on line 5-5 of Fig. 4.

ig. 6 is a plan view, with the outer cas-- ing in horizontal section. FFig. 7 is a detail section on line 77 of Fig. 8 is a d tail section on about the same plane as Fig. 5.

Fig. 9 is a detail side view from the right of Flg. 8.

Fig. 10 is a development, on a plane surface, of the rotatably shiftable controller.

Fig. 11 is a side view of certain external parts of the mechanism as arranged in a car.

Fig. 12 is a detail view similar to Fig. 5, but illustrating a modification in which provision is made for automatic shifting into reverse.

Fig. 13 is a detail plan view of parts shown in Fig. 12, with the selector disks in horizontal central section.

Fig. 14 is a detail side view from the right of Fig. 12.

- F'g. 14 is a detail horizontal section on line 1414 of Fig. 14.

Fig. 14 is a view similar to Fig. 14 but showing one of the parts in a different position.

Fig. 15 is a detail section of' parts shown in Fig. 14 but on a plane at right angles to that of the latter figure.

Fig. '16 is a development, on a plane surface, of the controller shown in Fig-10 as modified to provide for automatic shifting into reverse.

Fig. 17 is a detail side view showing the connection between the controller and the arm by which it is adjusted as the accelerator edal of the car is depressed or released.

Fig. 18 is a side view similar to Fig. 11, but showing releasable means to prevent the accelerator pedal from rising to reverse position when the foot is raised.

Referring first to Fig. 1, the shafts 10 and 11 are parallel and are rotating or rotatable in the directions of the arrows, shaft 10 having an axially stationary gear 12 and shaft 11 a gear 13 slidable on a helical spline 14. Assume thatgear 13 is slid leftwardly far enough to catch gear 12. Then if the pitch-line velocity of 12 is greater than that i of 13 the latter will be rotated at a faster ratethan its shaft 11 and inconsequence will be screwed leftwardly into complete mesh, coming up against a stop 13. If now the velocity of shaft 11 be increased or if the velocity of shaft 10 be decreased, so that the former tends to drive the latter, gear 13 will be unscrewed toward the right and thus will be unmeshed. In other words, if the driving torque of the engine is transmitted by gear 12 to gear 13, the power of the engine is utilized to mesh the gears after initial engagement, and the inertia of the car to unmesh the gears when the engine is exerting a braking effect on the car, or when a clutch-brake is applied.

Referring next to Figs. 2, 3 and3, the shaft 10 is connected by gears 15, 16 to shaft 17 which is driven by the engine (not shown) through a clutch 18. Shaft 10 also has fixed gears 12 and 27, and is also connected by gears 20, 21 to a shaft 22, which -may be the reverse-idler shaft, on which'is fixed a friction disk 23. Shaft 11, having 13 and 28 adapted to be shifted axially into and out of mesh with gears 12 and 27, respectively, is equipped with a friction .disk 24 overlapping disk 23 but spaced axially therefrom. It will be seen that when disk 23 is in motion the ratio of its angular speed to the angular speed of the driving gears 12, 27, is constant and is determined by the ra tio of the gears 20, 21. The angular-speed ratio between disk 24 and driven gears 13, '28, when in motion, is also constant and predetermined,'being unity since all those are on the same shaft. Between the two disks is a selector wheel 25, rotatable andslidable on a transverse shaft 26 by frictional engagement with the disks. Shaft 26 extends laterally from a vertical rod or stem 29, the shaft and rod forming a T-piece which can move vertically in both direct-ions in guides 31, 32. It will be understood that shaft 11 represents the shaft which in the conventional transmission drives the propeller shaft which in turn transmits the driving torque to the rear wheels of the car.

Consider now Fig. 3, which illustrates in diagrammatic end view the selector disks 23, 24, and the selector wheel 25, and-assume that the latter is above theline 22-11 through the'axes of the disks, say at a position where it isv in contact-with the disks at points in a line extending perpendicularly to the plane of 'the'figure through point 30 thereof. The movement of translation which would be imparted to the wheel by disk 24 alone at point 30 is represented in direction by the arrow a. Similarly the movement which would be imparted by the disk- 23 alone is represented'in direction by zero point.

velocities.

which of these components is the greater. By similar reasoning it can be shown that when the wheel is below the line 1122 its horizontal motion will be rightward and that its vertical motion will be up or' down according to the relative magnitudes of the When the wheel is on the line 1.l22 the horizontal components are zero, and somewhere on that line there is a pointat which, with a given speed-ratio between the disks, the positive upward and negative downward components are equal and therefore have zero as their vector sum. In such position the Wheel will rotate witht- .11? motion of translation. Evidently, as the speedratio changes, this zero point will shiftits position on the line. Hence there is such a pointfor every speed-ratio; and converse ly, for every point on the line there is a speed-ratio which will make the vector sum of the vertical components zero. It will also be clear that when the pitch-line velocities of gears 12 and 13 are equal the zero point then obtaining will be different from the zero point obtaining when the pitch line velocities of gears 27 and 28 are equal. In other words, each pair of gears has its own Assuming that there is no slippage between the wheel and the disks, that the disks are rota-ting at the same angular speed, and that the wheel is free to move in all directions, the path of the latter is a circle around the zero point as a center; and as this point shifts, the path of the wheel departs from the circular form. The actual values of the horizontal components of the motion of the wheel are functions of the angular speeds ofthe-disks and of the distance of the point of contact from the axial plane 1122, only, and are therefore independent of the horizontal distances from the point 30 to the centers of the disks.

. Similarly, the vertical components of the wheels motion are functions of angular ,speed of the disks and the horizontal distances of the point of contact (30) from the centers of the disks, only, and are therefore independent of the vertical distance of the wheel from the line 11 22. The above theory of the mechanism is derived from mathematical analysis, which it is deemeth unnecessary to repeat here. Suffice it to say that for the various disk-speed ratios obtaining when the gear p1tchl1ne velocities have unity or approximately unity ratio,

points can be found (below the line 1122) at which any increase of'the speed of disk 23 will make the sum of the aforesaid vertical components positive in sign, and the resulting upward movement of the wheel can be utilized to shift the gears. If the disk 24 is wide enough to overlap the axis of disk 23,

the wheel can be shifted by the disks to a position beyond the axis named. At such position disk 23 exerts a downward impulse on the wheel, even when disk 2i is stationary, and the resulting downward movement can be utilized to shift into reverse.

Reverting to Figs. 2 and 3, assume that the selector wheel 25 is below the plane of shafts 22, 11, that the wheel is held by some mechanical means (not shown) so that it cannot move horizontally; and that both disks 23, 24 are at rest, the engine idling, and the clutch 18 disengaged. The clutch is now engaged and the engine accelerated as usual in starting a car. starts. lVheel 25 then rises rapidly, and by suitable connection (not shown) with gear 13 slides the latter into initial mesh with gear 12 while the pitch-line velocity of the latter is still low and therefore but little greater than the zero-pitch-line velocity of gear 13. Further acceleration of shaft 10 starts the car and "at the same time the action of the helical spline 14 draws gear 13 into complete mesh, farther movement of the gear being prevented by the stop 13 on shaft 11. The car is thus started, with the transmission in low or first speed. At the instant of initial engagement of gears 13 and 12 the selector will bein a certain position, say at the point :0 in vertical line Z, which line may be taken to represent the horizontally, it will travel to the left until it is out of contact with disk 24, whereupon it may be allowed to drop below line 1122, say to the point w in vertical line 0 which may be taken to indicate the off position of the selector.

Assume now that gears 27 and 28 represent the intermediate gears, and that the car is in motion in low gear at a car-speed suitable for changing to a higher gear. Desiring to shift into intermediate or second speed, the driver closes the engine throttle, thereby reducing the speed of the fixed low gear 12 (the engine exerting a braking effect on the car) and causing the helical spline to shift the sliding low gear 13 out of mesh. The transmission is now in neutral, the engine is idling, and the fixed gear 27 is running at a lower pitch-line velocity than gear 28. Next he opens the throttle. By suitable connection (not shown) with the selector 25 the first movement of the throttle lever or,.pedal shifts the selector to a' position between the disks so as to be rotated thereby and impel ed right- 'wardly under a horizontalguide, not shown,

to a position beyond the line Z, say to a point Disk 23 now is, as stated, at point y in the line i, representing the intermediate-speed position of the selector. By the time it reaches this point or shortly afterward, the selector has, by reason of the increasing speed of disk 23 or the increasing radius of contact thereon,

or both, an upward velocity in excess of the downward velocity imparted by disk 24. At the line 2', the selector passes the horizontal guide and instantly-rises (along a vertical guide, not shown) to a position 3 and in so doing actuates a shifting fork, not shown, which slides intermediate gear 28 into initial engagement with gear 27. Further acceleration of the engine then causes the helical spline 14 to carry the gear into complete mesh and against stop 28 on shaft 11. The initial engagement of the gears being effected, the selector escapes the vertical guide just mentioned; and, having a leftward component of motion by reason of its position above the shafts 22, 11, the selector returns to off position'w in line 0, being kept above line 11-22 (Fig. 8) by a suitable guide, not shown, until it moves out of contact with disk 24.

The car is now in second speed, with the selector in off position. By similar ro- .cedure the gears may be shifted into hlgh carrying clutch member 29 into engagement with clutch member 29, but enough has been said to explain generally the function of the selector. The operation of shifting into high, shifting down, and shifting into reverse will be explained in detail hereinafter.

In practise certain of the various guides and stops that have to be shifted into different positions to guide and arrest the selector may be conveniently formed on a rotatable member or controller which can be turned manually to the various positions necessary.

Preferably, however, it is connected withthe foot throttle, as intimated above, so that the operation is controlled by the foot, leaving the hands entirely free. The controller. can be and preferably is so designed that the selector can never rise (and-thereby cause the initial engagement-of the gears) unless the gears are running at equal pitch-line velocities or at suchslightdifference of pitch the stop similarly numbered in Fig. 2.

When the intermediate sliding gear 28 is shifted leftwardly into mesh with the fixed intermediate gear 27 on countershaft 10, its

movement is limited by the grooved collar 43 coming up against the lugs 28. When the low sliding gear 13 is shifted rightwardly into mesh with reverse gear 44 the nut 45 on the hub of the sliding gear meets the lugs 28; and in the opposite movement, by which the low sliding gear is meshed with the fixed low gear 12, the former is arrested by the nut strikingthe bearing 40.

High speed is produced by shifting gear 28, Fig. 4, rightwardly to bring intern-a1 gear or clutch member 29 into engagement with external gear or clutch member 29, thus giving direct drive from shaft 17 As previously explained, when shaft 10 (Figs. 2 and 5) drives shaft 11 the sliding gear which is taking the driving torque tends to move leftwardly due to the helical splines; but it will be seen that in the case of the clutch members or high gears 29, 29 the direction of the splines is wrong and hence the latter tend to force the clutch mem bers out of instead of into mesh when shaft 17 is driving shaft 11 directly. Accordingly the teeth of the clutch members are also made helical in form, as indicated, with a pitch-angle enough greater than that of the splines to overcome the action of the latter and to overcome also the frictional resistance encountered.

The sliding gears 13, 28, Fig. 4, are shifted by means of forks 46, 47, fixed on horizontally' slidable shifter rods 48, 49, Fig. 6, which are locked in neutral by the usual spring plungers 50, 51. A look 52 is provided to permit only one gear to be slid intomesh at any one time. In-Fig. 6, rod 48 is in neutral and cannot be shifted until rod 49 is shifted to carry its gear 28 (Fig. 4) out of mesh. Rods 48, 49 'are shifted by the selector as explained hereinafter,or by a hand lever 53 in'the conventional manner. For this purpose the lever is'adapted to engage at will either collar 54 or collar 55, pinned on the respective rods.

The transmission can also be cleared, thatis, both sliding gears-can be brought into neutral, by depression of the clutch pedal, not shown. The devices provided to-accomplish this result'are shown in Figs. 4 and 6. Referring to these figures, forkedlever 56 is connectedin any convenient and suitable manner (preferably adjnstably) to shaft 57 carrying the fork 58 which, when the shaft is rocked by depression of the clutch pedal,

disengages clutch 18 against the tension of a spring 59. Lever 56, rocked by the same operation that disengages the clutch, cooperates with a collar 60 fixed on a short stem 61, slidably mounted, and fixed to an arm of a Z-shaped yoke 62, so that as collar 60 and stem 61 are actuated the yoke will be shifted on rods 48, 49. Block 63, which can slide on the rods named, is connected by rod 64, shiftable axially through yoke 62,

same time, yoke. 62 rocks lever 66 counter- I clockwise (Fig. 6) thereby sliding the block 65 rightwardly, which carries rod 64 and yoke 63 in the same direction. If, then, gear 13, Fig. 4, is in mesh with .gear 12, fork 46 will be in the path of rightwardly moving yoke 63 and will be shifted thereby,

thus unme'shing the gears nained. If gear 13 is in mesh with reverse gear 44, the fork will be in the path of yoke 62 and will be shifted leftwardly thereby, thus disengaging gear 13. Similarly, gear 28 will be shifted into neutral by yoke 62 or yoke 63 engaging fork 47, according as the gear is in mesh with high gear 29 or w th intermediate gear 27.

Selector disk 23, Fig. 7, is rotated by the reverse idler shaft 22 but is not mounted directly thereon. Instead, it is fixed on the outer end of a stud 69 which extends into the shaft (made in tubular form for the purpose) and has on its reduced inner portion a left-hand thread 70 cooperating with anut 71 held against rotation by a key 72 which also keys reverse gear 44 to the hollow shaft. Encircling stud 69 in front of nut 71 is aheavy spring 75 bearing against loose .Washers 73, 74, the latter resting against a split spring ring 76 in-an inner groove in the shaft. When the engine is dling ormoving very slowly with respect to the car,

disk 23 is moving very slowly-with respect to disk 24, and the latter thereforedrives the former (and stud 69 also) through selector wheel '25, fasterthan shaft 22. Under these circumstances nut 71 is backed off leftwardly, away from spring 75, the ex- ;pansion of which is limited by washer 73 hearing on a shoulder 77; .withthe result that disk 23 is urged rearwardly only by spring 78, in rear of nut 71. But when the throttle is 'opened and-.the-speed :of disk 23 is caused to exceed that of disk 24, theselector wheel (25) tends to move upward. Any

resistance to this motion holds back disk. 23, causing shaft 22 to run ahead of the,

disk, with the result that nut 71 isv screwed forwardly (toward'the right in Fig. 7), therebycompressing spring 7 5 until washer 7 3 strikes'the s acer 79 encircling the forward portion 0 stud 69. The pressure of spring 75 is thus addedto that ofspring '78 to hold disk 23 in contact' with selector wheel rovide the frictional force necessary to ena le the selector to shift the gears. -It is to be noted that in Fig. the selector wheel is shown in the off pos1t1on.

When"the clutch is disengaged, disk 23 is shifted forwardly to permit the ,,Se1ector tending laterally from the stem 29.

wheel to be moved into position between the disks without effort. This advanceof disk 23 is accomplished by yoke 62 (Fig; 6') striking the upper end of lever 80 (Figs. 4, 6 and 7) the lower end of which engages collar 81 and thus shifts stud. 69.

Disk 24 is fixed on the driving flange hub 11?,which is in turn keyed to shaft 11, as shown in Fig. 4.

The selector wheel 25- is mounted to rotate freely on a hollow stud 82-, jFigsI 5, 7 and 8, which is slidable on the splined arm 26 ex- Stud 82 is fixed on a vertical shifter-plate 83, so that as the selector-wheel 25 moves axially on arm 26 it will carry the plate with itto the various shifting positions from which the selector rises to shift the, gears. The upward and downward movements of the selector 2:) and plate ,83 are limited by the the guides 31, 32.

shoulders 84,855 .on the stem 29, striking 1 As before stated, the shift-ihg of the gears 13, 28, and 29 into initial engagement with gears 12, 27, 29, is effected by shifter. rods 48, 49. The latter are shifted by the selector plate 83 (itself-actuated by the selector wheel) through the mediumof. parts which will now be described.

Above the splined arm 26 on whichthe selector wheel rotates is a'transverse shaft 86 (Figs. 4, 5, 8 and 9) on which is mounted a pair of shifter levers 87 88, having upwardly extending-arms 87, -88, cooperat- I ing respectively with the shifter collars 55 and 54. The latter, it'will beremembered,"

actuate the shifter rods 49 and 48 which in turn actuate the shifter forks 47 and 46 (Figs. 4 and 6)., The levers 87, 88 have branched. lower arms. When the selector wheel is in the low position itis inf -the 1'' plane of line Z, Fig. 8. In this position the plate83 is, in theplaneof cam-arm. 88 'of lever 88, so that when the plate rises its cam-finger 83 will;engage the-*cam-arin mentioned and rock. the lever 88, which in turn shifts 'rod 48 toward the'left 6) and thereby slides gear"13 (Fig. 4). into initial mesh" with gear 12, after which "completeengagement 1s produced by, the action of the helical splines on shaft 11. I'Ii'this upward movement of plate 83-it is" prevented from moving horizontally by a controller, described hereinafter, but'yas it' 'reaches its upper positionit escapes the "controller,

whereupon the selector wheel'25, being then above the axial plane of the disks 23,24,

-moves leftwardly until it" strikesthe" lower armfl88 of lever 88. "By this time, however, the wheel has also a downward component of motion, due to the deoreas'eofthe radius of contact on'disk 23. Hence'whenthe plate 83 is'arrested by stop 88 the"wheel'j(and plate) move' downwardly, escaping the stop and then ieontlnuing their leftward and L as downward movement to the off position represented by'line 0, Fig. 8. In this position the selector wheel 25 is entirely disengaged from both disks, as indicated in Fig. 7.

' To shift from low into intermediate.

(the car having been accelerated to a speed suitable for intermediate gear) the engine is throttled down, thereby causing gear 13 to go into neutral by the action of the helical splines. The accelerator pedal is then de' pressed. The first effect of the latter operation is to draw the selector wheel into engagement with the disks, causing it to move rightwardly (Fig. 8) past low? to the in.- termediate position indicated by the line i. To permit easy movement of the wheel from its off position into engagement with the disks the latter are each provided (Fig.7) with a slight chamfer, as 23, 24*, which is less than the angle of friction.- As soon as the disks begin tomove the selector, the engine throttle is opened and the disk 23 begins to speed up, so that when the selector reaches position i, or shortly after, it will move upwardly, bringing cam-finger 83 against cam-arm 87 on lever 87, thereby rocking the latter and shifting gear 28 into initial mesh with gear 27 through the agency of collar 55,- shifter rod 49, and fork 47. Its upward movement completed, the selector moves to the ofi position.

In shifting from intermediate into high,

the selector moves past the low and intermediate positions to higlrposition, h, Fig. 8, then rises and brings cam-finger 83 (see also Fig. 9) into engagement with camarm 87 on lever 8'7.- This action rocks lever 87, which in turn shifts rod 49 and fork 47 rightwardly (Fig. 6), carrying gear 28 in the same direction (Fig. 4) and bringing ,clutch member 29 into initial engagement with member 29. The latter parts are then,

drawn into complete mesh by the action of their helical teeth, as previously explained,

and the selector returnsto its off position.

The controller, by which the selector wheel is guided and limited in its motion, is shown '-9l.arranged between the selector disks l lector wheel slides.

at 90, Figs. 4, 5; 7, 8, 9 and 10, and comprises a circuinferentially and axially slotted member f xed on a transverse rock-shaft 2? 24 and below the stem 26 on which the se The outer end of' the shaft is connected by a crank 921(Figs. 5 and '11) and adjustable link 93 to the lower end of a lever 94 which is fulcrumed at 95 on the forwardly ciuw'ed lower end of the accelerator pedal or foot-throttle lever '96, the

:latter being pivoted on theunderside of the floor-boards 97. The upper end of lever 94 is connected by link 98 to an arm 99 which is intended to represent the throttle valve lever of the internal combustion engine or motor 100. Springs 101, .102 are parts yieldingly in position 12, thereby rocking arm 92 and controller 90 counterclockwise. During this operation, link 98 is held from leftward movement by its stop 103 which bears against a bent finger 104 on the pedal. Further depression of the pedal permits the stop to pass the finger, permitting the lever 94 to move bodily, say as far as position 0, thus rocking the controller still farther and at the same time opening the throttle valve of the engine.

When the controller is in position 1, Fig. 10, with the selector wheel'in off position, Fig. 7, the downwardly extending finger 105 on the selector plate 83 is in the left hand portion (see. also Figs. 5, 7 and 8) of the helical controller-slot 106,-.-but asthe' controller is rocked by depression of the ac- 7 celerator pedal the cam action of the slot carries the finger, and with itthe selector plate and selector wheel, rightwardly until the finger meets the controller-stop 107, whereupon the rightward movement of the selector ceases and the controller notch 108 embraces the selector plate finger, preventing movement of the finger in either hori- L zontal direction. The selector isthen in 'low position, indicated by the line so marked in Fig. 10. The acceleration of the engine now speeds up disk 23; and when the pitch-line velocity of gear 12 has the proper ratio to the 'itch-line velocity of gear 13 the selector rises and shifts the gears into initial engagement. Preferably the posi-' tions of the selector are so chosen that the ratios at which the selector, rises are someing aligned with the spaces on the other, the

two would not mesh, and it might so happen that this condition would exist for an appreciable time. To aid in meshing the gears under such conditions the teeth may have the usual chamfer at their meeting edges. Pref-- erably, also, they are made to meet with a velocity ratio which is slightly greater than unity, so that the non-sliding gear-will be 7 running ahead. Hence the teeth on the two can never be lined up for more than a fraction of a second, and the initial engagement will in all cases be produced practically at the very instant the gears meet.

As the initial engagement of the gears 13 and 12 is effected the finger on the upwardly moving selector plate escapes from notch or slot 108 (Fig. 8) and the selector returns to off position as already described, while the controller itself, under the action of spring 101, Fig, 11, and being no longer restrained by the finger, swings over to position 3,-Fig. 10. p

To shift into second or intermediate speed the throttle is closed by. taking the foot off the accelerator momentarily. This permits the controller to return to initial position (1, Fig. 10) whereupon the finger drops into the slot 106. When the pedal is again depressed the finger is drawn rightwardlyby the slot and the selector moves to low position in slot 108, but, the throttle being still closed to idling position, the selector does not, risevout of the slot, since the downward-impulse exerted by the disk 24 exceeds the upward impulse exerted by the-disk 23. The pedal is now released and quickly depressed again. The first action permits the controller to swing (clockwise,

Fig. 11) toward position 1, Fig. 10, until the edge 109 of longitudinal slot 110 strikes the selector finger, whereupon the selector movesagain toward the right, until it is arrested by stop 111, at which point the depression of the pedal carries intermediate notch or slot 112 down over the finger. The engine, being accelerated" by the opening of the throttle, speeds up the gear 27, Fig. 4, and when the now increasing ratio between the pitch-line velocities of gears 27 and 28 reaches the proper predetermined value the selector moves up and shifts the gears into initial engagement. At the same time the finger 105 escapes from slot 112 and the selector returns to its oif posit-ion, and the controller, no longer restrained by the finger, swings on to position 3 (Fig. 10) under the tension of spring 101 as previously described.

To shift into 'high the operation is the same, except that the accelerator pedal is released and depressed three times instead of twice." The xsecond-release and depression brings the selector finger into the intermediate or second speed notch 112. The third release carries the notch away from the selector finger and brings the edge 113 of longitudinal. slot 114 against the finger whereupon the selector moves toward the right until .arrested by stop 115 at the end of slot 114, The third depression of the pedal carries the high speed slot 'or notch 116 over the finger, and when the pitchline velocity-ratio of clutch members 29 and 29 has the right value, that is, when the Q angular velocities of shafts 11 and 17 are j jeq-ual, the selector rises and shifts the gears into initial engagement. The selector finger then escapes from notch or slot 116 and returns to its ofi position, while the con troller swings on to position 3, Fig. 10, as already described.

In shifting down, say from high to second speed, the opera-tion is the same as in shifting up from second to high except that the third release and depression of the accelerator pedal is omitted, and, instead, the operator at the second depression merely presses the pedal far enough to speed up the engine, thereby accelerating gear 27. When its pitch-line velocity has the proper ratio to that of gear 28 the selector rises and effects the initial shift. In shifting down from second to low, the second and third operations of the accelerator are omittedand the motor is speeded up at the first depression of the pedal.

In practise the operation of shifting into high need not involve three distinct actu ations (up and down) of the accelerator pedal. If the pedal is depressed lightly, ]ust far enough to bring the selector wheel between the disks, the wheel will move into intermediate shifting position without being engaged by the low'slot 108, and when it drops into the slot 114 the impulse can be felt. Further depression ofthe selector. to rise (finger 105 being engaged pedal immediately afterward will then cause the and guided by slot 116) and shift the gears into high. The driver soon learns to operate the controller by the feel of the action. The movements of the selector are extremely rapid, with no appreciable lag behind the movement of the controller, so that if the engine has good pick-up the gears can be shifted as fast as the driver can operate the pedal.

It will be seen that the function of the controller 90 is chiefly to guide the selector in the automatic movement thereof and to limit the axial movement of the selector. It shifts the selector (by means'of the helical cam slot 106) from ofi position int-o engagement with the disks. When the car is at rest, with the clutch disengaged and the selector disk 23 advanced, the controller not only carries the selector to a position between the disks but also carries it on t the low position; but after the car is started the controller does not shift the selector except to bring it into engagementwith the disks. From that time on, the selector is moved by the energy exerted upon it by the disks. In other words, the controller cannot force the selector into any position except into low, and then only when Disk 24 is at rest and hence exerts no downward impulse upon the wheel, while disk 23 is rotating and hence exerts an unopposed upward impulse, with the result that the selector will rise at the instant it engages disk 23 and will carry finger 105 out of slot 100 so that the controller will have no further control over the finger and selector. It is therefore impossible to move the selector intolow position with the car at rest unless the clutch is disengaged. Again, suppose that after accelerating the car in low and starting to go into second, the speed of the engine (and of gear 27) is too great for shifting. In that' case the excessive speed of disk 23 will cause the selector to rise before the guiding finger 105 reaches the stop 111; and, rising above the plane of the axes of the two disks without its horizontal motion being restrained by slot 112, the selector will move leftwardly toward off position without actuating the shifter fork. Hence, to get the selector into intermediate or second position the speedof the gear 27 must be reduced by throttling down the engine. It will thus be seen that the action of the controller-selector combination is practically proof against improper operation, it being impossible to put a pair of gears in mesh when one of them is running too fast or too slow, or to damage gears or selector.

The controller 90 (Figs. 7 and 10), has three surfaces, at three different levels,-so to speak, with respect to the axis of the controller. These surfaces are indicated by the shadings in Fig. 10. The heavily shaded portion indicates a surface which is so low that when the finger 105- (Fig. 5) is in contact with it'the selector-wheel axis is below the axial plane of the disks, and when in this position the wheel tends to travel toward the right. After rising above the axial plane mentioned, the selector finger moves toward the left unless prevented by one or another of the slots 108, 112, 116. If, after reaching one of these slots, its upward component of velocity in sufficient to carry it up out of the slot, it immediately moves leftward, and if at any time thereafter its upward component decreases fast enough to let the finger fall upon the controller the finger will find directly under it the next higher surface forming the bottom of slot 117, represented'by the lighter shading, for the reason that as soon as the finger rises out of the slot. or notch the spring 101 (Fig. 11) in'lmediately swings the controller over to position 3, Fig. 10. This surface is high enough to prevent the selector from descending below the axial'plane of the disks and hence it must continue its leftward move ment to the off position. At the left of slot 117 are two inclines 117 and 117 designed to exert a calnming action on the finger and thereby positively compel the selector to move off of disk 24 to the position indicated by the line marked 01f in Fig. 10. The

highest'surface of the controller is unshaded,.

and the finger can never rise above it by reason of collar 84 on stem 29, Fig. 5, which collar is desinged to meet the guide 31 just before the lower end of the finger would rise above the unshaded surface.

In the embodiment illustrated in Figs. 4 to 11, shifting into reverse is accomplished by the hand or foot of the operator, by means of the hand-actuated lever 53, Figs. 4, 5, and'11, or pedal 119, Fig. 11. The

lever has the conventional ball-and-socket universal mounting, so that it can pick up pinned to shaft 86, which is connected with the alignedv shaft 121 by a lost-motion clutch composed of two members 122, 123 pinned to the't-wo shafts. On the outer end of shaft 121 is a crank-arm 124 connected directly to the pedal 119. Hence depression of the pedal first takes up the play in the clutch, then rocks the shaft 86 and lever 88 clockwise, thereby advancing shifter rod 48 and shifting gear 13, Fig. 4, into initial engagement with the reverse idler gear 44 driven by gear 125 on the countershaft 10. The play in the clutch'permits shifting into low gear without affecting arm 124. Pedal 119 is locked so long as the clutch 18 (Fig. 4) is engaged. For this purpose shaft 57 is provided with an arm 126 to which is pivoted a locking bolt 127 extending rearwardly through a fixed guide 128 and into a downwardly open slot in the arm 124. When shaft 57 is rocked by disengaging the clutch, locking bolt or rod 127 is advanced, thus freeing shaft 121 and permitting-the same to be rocked by thepeclal. The mechanism just described prevents shifting into reverse while the clutch is engaged and thus prevents the possible damage which that operation might cause.

In the modification illustrated in Figs. 12 to 18 inclusive, provision is made for auto- .matic shifting intoreverse, under control of the accelerator pedal, as in the case of the forward speeds. For this purpose disks 23 and 24 are provided with circular grooves 130, 131, which define the off position which the selector wheel 25 takes after shifting into a forward speed. If, by means of l the controller (the clutch being disengaged),- the selector is shifted farther leftwardly, re-engagement of the clutch will bring the disks and selector again. to contact, whereupon the selector will again rise since when reverse is attempted the car and hence disk 24 are motionless and the latter is therefore exerting no downward impulse on the wheel. After shifting into reverse, the wheel again moves leftwardly to another .oif position, 12., indicated by the dotted position of the wheel in Fig. 13. When it is desired to shift into low forward speed the clutch is disengaged, thus separating the disks and permitting the controller to draw the selector wheel rightwardly past the grooves 130, 131 (or neutral position of the selector) to the low forward position, as previously described.

To enable the controller 90, Fig. 16, to shift the selector leftwardly beyond the neutral position a, Fig. 13, the helical slot 106 is extended leftwardly, and provision is made for a backward rocking movement of the controller, corresponding to an upward movement in Fig. 16. 'For this purpose the normal upper (or neutral) position of the accelerator pedal 132, Fig. 18, is determined by the spring-actuated clip 133. ltf this is kicked off the springs at once rock the pedal to the reverse? position indicated in dotted lines, at the same time rocking the arm 92 counter-clockwise from its oil position. This arm is geared to shaft 91, as shown in Fig. 17, so that-the counterclockwise movement of the arm gives the controller a clockwise movement, which by 7 the agency of the cam slot 106 shifts tlie finger 105 toward the left and with it the selector 25. When the pedal is again depressed, to accelerate in reverse or (the car having been stopped and the clutch disengaged) to shift into low and start the car, the vclip o1 detent 133 snaps down to its normal position, and thereafter prevents the pedal from rising to reverse position when the foot is raised.

To shift sliding gear 13 (Fig.4) into mesh with the reverse gear 44 the fork 46' must be shifted rightwardly. This is effected by the horn 83 of ,selector plate 83 (Fig. 14) actuating cam-arm 88 of forked lever 88. To insure leftward movement of the selector to the reverse off position after shifting, the selector plate is provided with a bevel 83 between its'horns, which, cooperating with the correspondingly bev eled depending finger 88 on lever 88, cams the plate and selector toward the left as they rise under the combined impulses of disk -3, which always rotates counterclockwise, and of disk 24 which now (the car be ing in motion backwards) rotates clockwise. As soon as the selector escapes both disks it falls by its own weight to a position below the axial plane of the disks and the finger 105 then rests on the heavily shaded surface at the left end of slot 106.

The lever 53, Figs. 14, 14 and 15, has

engaging either, but at their ends the collars are provided with inwardly extending lugs 137, 138, 139, 140. In shifting by hand, the lever is rocked transversely into one or the other of the notches 141, 142. Normally the lever stands in the position shown in Fig. 14 and remains in such position when the gears are shifted by the automatic mechanism. Thus Fig. 14 shows the position of the collars after collar 55 has been actuated to put the gears in high, but it Will-be observed that the lever remains in its neutral position. Then if it is desired to shift the gears into neutral by hand it is not necessary to know which gears are in mesh and then hunt for the proper notch, ,141 or 142 as the case may be. Instead, the operator simply swings the lever back and forth between the collars without. rocking it laterally. The lever then engages whichever lug (137, 138, 139 or 140) is in its path and shifts the collar as far at it will go. lhe engaging end of the lever is too narrow to permit engagement with both notches 141, 142 at the same time, and its amplitude of fore-and-aft swing is too limited (as by the ball-andsocket mounting, Fig. 14) to permit shifting the collars past their neutral position by engagement with their lugs. In short, to shift into mesh, the lever must be swung into one of the notches. Mere rocking of the lever forwardly and rearwardly can" only restore a pair of meshed gears to neutral.

To hold the lever 53? 'yieldingly in its normal position, Figs. 14 and 15, it is provided with spring locks of the ball type, indicated at 143, 144, which engage spherical recesses 145, 146, in the ball of the lever. lit will be understood that the locks are spaced angularly 90 apart, so that a substantial efiort (exerted on a handle, not shown, inserted in socket 120) will be required to swing the lever in either direction out of its normal position. It is to be understood that the hand-shift mechanism .described in this and the preceding paragraph can be used interchangeably with. the devices illustrated mesh by relative axial movement, of means acting automatically to cause such relative movement and dependent for operation upon a predetermined pitch-line velocity ratio of the gears.

2-. In a transmission mechanism, the combination with a pair of gears shiftable into mesh by relative axial movement, of a device acting automatically to cause such relative movement and dependent for operation upon a predetermined pitch-line velocity ratio of the gears, and controlling means operable at willto control the action of said "device.

3. In a transmission mechanism, the-combination with a plurality of driving gears and a plurality of driven gears, shiftable into mesh in pairs by relative axial movement, of a device acting automatically to cause such relative movement of a pair of gears and dependent for operationupon a predetermined pitch-line velocity ratio of the gears, and controlling means operable at willto determine which pair of gears will be meshed.

t. In a transmission mechanism, the combination with a pair of gears shiftable into meshby relative axial movement; of means acting automatically to cause an initial relative movement of the gears when the pitch- "line velocities thereof have a predetermined ratio, to effect initial or partial engagement of the gears; and automatic means utilizing the rotary motion of the gears to complete the relative movement and produce complete engagement.

-5. In a transmission mechanism, the combination with a pair of shafts, and a pair of gears thereon, shiftable into mesh by relative axial movement, of means acting automatically to cause an initial relative movement when the pitch-line velocities of the gears have a predetermined ratio, and a helical spline on at least one of the shafts to cause complete axial movement of the gear thereon after the gears have been in- 1tia1ly engaged.

' 6. In a transmission mechanism, the combination with pair of gears on separate shafts, one of the gears being shiftable axially into and out of mesh with the other; of adevice acting automatically to cause an initial axial movement of the shiftablegear when the pitch-line velocities of the two have 'a predetermined ratio;"and a helical .spline on the shaft carrying the shiftable gear, to complete the shifting movement when the other gear begins to drive the least one of the gears to move the same ax;

ially into engagement with the other.

8. In a transmission mechanism, the combination with a plurality of driving gears and a plurality of driven gears, shiftable into mesh in pairs by relative axial movement; of means acting automatically to cause such relative movement ofa pair of gears, said means including a pair of overlapping spaced disks rotating in harmony with the driving gears and driven gears respectively, a wheel between thedisks for rotation thereby and adapted to be shifted thereby axially and transversely, andshifting mechanism actuated by the wheel to produce the aforesaid relative axial movement of one or another pair. of gears according to' the extent of the axial movement of the wheel; and means operable at will to determine the extent of the axial movement of the wheel.

9. In a transmission mechanism, the combination with a pair of gears shiftable into mesh by relative axial movement; of means acting automatically to cause such relative movement and thereby effect a partial engagement of the gears,'said means including a-pair of overlapping axially spaced disks rotating in harmony with the gears, a re-.

volving member between the disks, rotated by thedi'sks and shiftable thereby, and shifting mechanism connecting said member with at least one of the gears to move the same axially into partial engagement with the other; and automatic means utilizing the rotary motion of the gears to complete said axial movement and produce complete engagement of the gears.

10. In a transmission mechanism, the combination with a driving gear and adriven gear one of which is slidableaxially into mesh with the other a disk rotating in harmony with the driving gear; a second disk, overlapping the first, and rotating in harmony with the driven gear and in the same direction as the first disk; a selector Wheel movable axially and transversely between the disks'and rotated by frictional engagement therewith; shifting mechanism connecting the selector wheel with the slidable gear to shift the latter into mesh with the

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